Hydraulic variable speed power transmitting mechanism



July 13, 1937. H. A. CENTERVALL' HYDRAULIC VARIABLE SPEED POW-ER TRANSMITTING MECHANISM Fiie d July 11, 1931 5 Sheets-Sheet 1 5% may "INVENTOR ATTORNE July 13, 1937. H. A. CENTERVALL 2,086,535

HYDRAULIC VARIABLE SPEED POWER TRANSMITTING MECHANISM I Filed Jhl I1, 1931 I 5 Sheets-Sheet 2 IN VEN TOR d, W

firm, W.

A TTORNE July 13, 11937. H. A. CENTERVALL 2,086,535

HYDRAULIC VARIABLE SPEED POWER TRANSMITTING MECHANISM 5 Sheets-Sheet 3 Filed July 11, 1951 INVENTOR a. W BY Mi Mi ATTORNEY July 13, 1937.

H. A. CENTERVALL HYDRAULIC VARIABLE SPEED POWER TRANSMITTING MECHANISM Filed July 11, 1951 5 Sheets-Sheet 4 INVENTOR WW A ORNE July 13, 1937. H. A. CENTERVALL 2,086,535

HYDRAULIC VARIABLE SPEED POWER TRANSMITTING MECHANISM Filed July 11", 1931 5 Sheets-Sheet 5 W 3462a? 2?e Z 345 21/ INVENTOR A? 4. W411- ATTORNEY means of supporting the variable stroke crank Patented July 13, 1937 PATENT. OFFICE HYDRAULIC VARIABLE SPEED POWER TRANSMITTING MECHANISM Hugo A. Centervall, New York, N. Y., assignor to Manly Corporation, NewYork, N. Y., a corporation of Delaware Application July 11, 1931, Serial No. 550,198

11 Claims.

This invention relates to hydraulic mechanism for the transmission of power at variable speeds and this application is in part a continuation of -my co-pending application, Serial No. 368,706, for Hydraulic variable-speed powertransmitting mechanisms, filed June 5, 1929.

The use of hydraulic transmission devices, wherein use is made of a power driven pump for forcing a current of liquid into the cylinders of a. motor operatively connected with the driving shaft of whatever mechanism is to be operated, control of the speed of the driven member being effected by varying the pump stroke is becoming 1ncreasingly widespread.

Great dimculty'has been encountered, however, in the operation of known hydraulic transmission devices due tooverheating caused principally by friction of the parts and the frictional resistance offered to the flow of the liquid, generally oil, through the various channels, ports and valves. This heat, generated from these or any other causes, hasresulted in serious impair-' ment of the efficiency of the devices, both because of the deteriorating effect upon the oil and the changing of its viscosity and further because of the expansion of the metal parts, which are necessarily close fitting, causing binding of the parts, or leakage, or both. The amount of suchoverheating is recognized as limiting the capacity of a machine of this class to transmit power continuously.

It is with the above facts in view that I have devised the present mechanism which has for its tating the dissipation of anyheat that is gen-- erated.

Another object is the provision 'of liquid recovering, replenishing and circulatory means which not only makes for economy of operation,

' but utilizes the air currents set up by the rotating parts to cool the liquid used-in this system.

A further object is to provide an improved element.

A still further object is to provide a device with an improved arrangement of parts, which permits each cylinder to be separately demounted and which permits the assembly oi all the parts with a minimum of time and effort.

Other objects and novel features of this invenarranged, showing an improved and alternative I C provided with means for establishing and contion will be pointed out and clearly defined in the claims at the close of this specification;

In the drawings:-

Fig. 1 is a top plan view of a complete hydraulic transmission mechanism constructed in accord- 5 ance with my invention.

Fig. 2 is a central vertical longitudinal sectional View.

Fig. 3 is a vertical cross-sectional view through the pump unit, the view being taken along the line 3-3 of Fig. 2. I 1

Fig. 4 is a similar view taken through the stationary intermediate member located between the pump and motor units, on the line 4-4 of Fig. 2.

Fig. -5 is a vertical section taken on the line 15 5--5 of Fig. 2, illustrating part of the slidable pump stroke varying member in detail.

Fig. 6 is a detail cross-section on the line 6-6 of Fig. 2, showing the mounting for one end of the variable stroke crank element of the pump.

Fig. '7 is a cross-section on the line l--1 of Fig. 2.

Fig. 8 is a vertical section on the line 8-8 of Fig. v5. 2

Fig; 9 is a vertical section, partly schematically form of fluid collection, replenishment and circulatory system.

Fig. 10 is a detailed view of. a valve device.

Fig. 11 is a top plan view of guide means for the valve like that shown in Fig. 10.

Referring more particularly to the drawings, I have shown. the device as comprising, broadly, a pump unit A, a motor unit B indirectly driven thereby, and an interposed stationary member trolling communication between the pump and motor units.

The machine is carried by a stationary frame including a member Hi from which extend prefer- 40 ably diverging arms ll secured to a transverse end plate I! outwardly of which is located a casing member I3 secured thereto and cooperating therewith to define a sump l4. Secured against one face of the member I 0 and located between I the arms I l is a member l5 formed centrally with a cylindrical or trii'nniondike member [6. Secured to the opposite side ;of the member In is a similar member I! formed centrally with a trunnion-like. member I8'and which constitutes the support for the motor unit B.

The pump unit A iscarried by the members l2 and i5 and comprises a hollow rotor I! of cylindrical shape having a hub portion 20 surrounding the trunnion member 15 and located within an 5 roller bearing structure'ZB is interposed between this end of the rotor and the hub 25. By this mounting, the rotor is adequately sustained by the I stationary parts for rotation with respect thereto.

The rotor assembly further includes a series of radial cylinders 21 which are closed at their outer ends except for ports -28 and which have their inner ends fitting into openings 28 in the rotor l9. These cylinders are preferably individually removable and are consequently represented as having attaching base portions 38 secured on the periphery of the'rotor l9 as by cap screws 3|. Removably secured to the sides of the cylinders at the ports 28 therein are hollow arms 32 which constitute conduits and which have their other ends secured to the hub 28 at ports 33 therein, suitable packing being used at these joints to make them fluid tight. These hollow arms, like the cylinders, have attaching portions 34 secured to the hub as by cap screws 35. Any desired number of cylinders, together with the corresponding arms 32, may be provided. In the preferred form I have shown the pump A as having seven cylinders.

Slidable within the cylinders 21 are pistons 36 connected by wrist pins 31 to connecting rods 38 which have their inner ends enlarged to form shoes or base portions ,39. These shoes 39 are disposed against the outer periphery of a ring 48 to which they are held by means of a pair of rings 4| located atopposite sides of the series of connecting rods and fitting within grooves 42 in the shoes 39. The shoes 39 may slide circumferentially with respect to the ring 48 for auto-- matically accommodating themselves to thevarious conditions brought about by movement of the stroke varying means to be described.

The means for driving the pump A'comprises a drive shaft 43 passing through a stufling box 44 located in a pocket 45 in the casing l3. Adjacent to the inner end of this' shaft is a disk 41 preferably formed integrally with the shaft 43 and which is secured to the rotor I!) at the face of the hub 20 thereof, as shown at 48. The inner end of the shaft 43 extends into a recess 4:9 in the free end of the trunnion member l6, roller bearing'assemblies 58 being interposed between the shaft and the cylindrical wall of the recess. The shaft 43 is additionally supported by a spider 5| which has its legs terminating in attaching feet 52 secured to the outer face of the end plate l2 and which has a hub portion 53 containing a ball bearing assembly 54 surrounding the shaft.

The means for controlling the reciprocation of V thepistons 36 to whatever extent-is desired, is an important feature of my invention. It may be broadly described as a crank pin mounted so that it may be moved transversely of the machine to determine the axis about which the piston assem-- bly rotates. This mechanism comprises a hollow laterally movable crank pin 56 supportedon its front end by a relatively large and rugged platelike member or slide 55 and supported on its inner end upon the drive shaft 43 by intermediate means later to be described. The position of this mechanism determines the length and direction of the stroke of the pistons'36. The crank pin. 56 and the upper central portion ofthe slide 55 are slots 15 are of such size and shape as to permit the maximum desired lateralmovement of the crank pin 56 and the slide 55 without bringing the inner.

peripheries of said slots into contact with the.

drive shaft 43. g I v The sleeve 56terminates on one end in a somewhat disk-like vertically elongated portion 51 having spaced overhanging flanges 58 at the top and bottom and located adjacent the disk 41. Each flange 58 is fitted with a guide 88, pinned as at 61 in the longitudinal slots 61a. Since the opposing faces of the flanges 58 and the guides 66 are similarly curved, these parts may rock slightly with respect to one another to permit a slight adjustment between the parts, but the flanges 58 and the guides 66 will be held firmly in place as regards any motion transverse of the machine. The guides 66, which may be made of bronze or any other suitable material, are slidably by the hub 68. formed on the slide 55 and keyed as at 6|. The inner end of the hub 68 is preferably tapered toward the axis so as not to interfere with a retaining ring 64 which is carried by the member l9 and which holds the above described roller bearing assembly 26 in place. a

The slide 55 is movably mounted against the end plate l2 and is provided with downward extensions 69 terminating at. their lower ends in laterally arranged lugs or feet 10 slidably fltting within elongated slots 1 I in the end plate I2, these slots being covered by plates 12. The downward extensions-69 are preferably widely spaced so as to resist any tendency to be. angularly displaced. The slide 55-is held in place against the end plate l2 by the angled retaining members 13, secured as at 14 to the end plate l2 and overlying the outer faces- .of the extensions 69. The lugs 16,

the slots H and the members 13 cooperate to permit the slide to be easily moved laterally of the machine but to hold said slide firmly in position as regards any other displacement. Suitable stopping means of any sort may be employed to limit the lateral motion of the slide 55 and of the parts moved by its It will be seen thatI have provided a laterally slidable crank mechanism firmly supported on both its ends, said support coming at either side of the center of pressure of the pump piston assembly. It will also be noted that the support afforded by the assembly cooperating with the disk-like portion 51 and by the feet or lugs I8 of the slide 55 form a final supporting means of .triangular relation to each other, giving in eifect 86 for the roller bearing is mounted on the end of The inner periphery of the plate 88 the flange. is hollowed out to contain a felt washer to prethreaded through the collar 94 and accessible for vent leakage of any oil which may get past the bearing 85. The other or outer end of the rotor 82 is closed by a plate 81 secured thereto, this plate carrying a stub shaft 88 which constitutes the driven shaft of the machine. As it is necessary to support the rotor 82 at a plurality of points, I have shown its intermediate portion as containing a roller, bearing assembly 89 engaging upon areduced step on the trunnion like mem-' ber I8. The bearing assembly 89 is held in place by the retaining ring 91 cooperating with the rotor 82. Beyond this-step 90 the trunnion member is reduced to form an eccentric spindle 91 upon the preferably tapered end 92 of which is secured, as by a nut 93, an eccentric collar 94 uponwhich is mounted a ball bearing assembly engaging against and supporting the outer end of the rotor 82. The eccentric collar 94 has a flange 96 at its inner end which cooperates with c the plate 8 1-to retain the ball bearing assembly in place.

The motor unit further includes a plurality "of cylinders 98 having their outer ends closed except for ports I02 and having their inner ends fitting within openings 99 in the periphery of the rotor 82. As these cylinders are, like the pump cylinders, intended to be individually detachable, they are shown as having attaching portions I00 secured to the outer periphery of the rotor by the cap screws IOI. Detachably mounted on the sides of the cylinders 98 at the ports I02 therein are curved hollow arms I03 constituting-conduits, and these arms are secured to the hub portion 83 at ports I04 therein. The arms have attaching 7 portions I05 secured as by cap screws I06.

Slidable within the cylinders 98 are pistons I01 carried by connecting rods I08 which have their inner ends provided with shoes I 09 slidably bearing upon a ring I I0 and held in place by a pair of retainin rings II I at opposite sides of the piston rods and seated within grooves H2 in the shoes. Within the ring H0 is a rollerbearing structure II3 engaged about the spindle 9I.. This roller bearing assembly is prevented from displacement inone direction by the ring 91 and in the other direction by a ring 'II4 engaged by screws II5 adjustment uponremoval of the plate 81,

In order that there may be proper timed communication between the pump A and the motor B, the trunnion member I6 is formed with a pair of ports H6 and H1 separated by a transverse partition II8, these ports being adapted to register with the ports 33 in the hub 20 of the pump rotor I9. Similarly the trunnion member I8 is formed with ports H9 and I20 separated by a corresponding partition member and adapted to register with the ports I04 in the hub 83 of the motor rotor 82. Formed through the central member I0 and through the'trunnion members I6 and I8 are aligned longitudinally extending passages I 2| and I22, the former communicating at their ends with the ports H6 and H9 and the latter communicating at their ends with the ports [I1 and I20; The members I6 and I8 with their passages and ports constitute and will be claimed as valves. The portion of the central stationary member I0 containing the passages I2I and I22 is supported by the webs I80 (see Fig. 4) of elliptical cross section and by the smaller webs I18 and I19, thus forming intercommunicating chambers I15. It will benoted the webs I18 and I19 are substantially in line with the passages I2I and I22 respectively, allowing other fluid connections to be made with these passages as will be later explained.

The operation of the hereinbefore described parts is as follows: Y

The drive shaft 43 is connected to any suitable source of power and in this embodiment is supposed to be rotating in clockwise direction. As the drive shaft 43 is rotated, it carries with it the plate 41 which in turn rotates the pump rotor I9 and the cylinders 21 and the arms 32 which are part of the pump rotor assembly. Obviously, during each revolution of the rotor, the ports 33 fat one time will be in communication with the port IIS and at another time with the port I I1' of the member I6. As the cylinders 21 rotate they carry with them the pistons 36 and the connecting rods 38. On the exhaust stroke the shoes 39 will 'be held in place against the ring 40 by the pres- .sure exerted upon them by the fluid in the cyln inders 21 through the pistons and connecting rods and on the suction stroke, the shoes 39 will be heldin place by asimilar but lower pressure, or, if such pressure be insuflicient, by the rings 4|.

.The ring 40 will also rotate on the hearing assembly 59. The only movement of the shoes 39 on the ring 40 will be the small amount of sliding necessary to compensate for the varying angularities of the connecting rods at the various points in its pathof travel.

If the crank pin 56 is in its middle position or so that its center coincides with the axis of the rotor I9, the cylinders 21 and thepistons 36 will obviously be rotating about a common center and there will be no reciprocation of the pistons. The

pump A is then in its zero or no stroke position perform one complete intake stroke and one com-.

plete exhaust stroke for each revolution of the rotor I9. The length of the stroke will depend upon the distance the slide 55 and the crank pin 56 has been shifted. In the present embodiment,

with the crank pin shifted to the left, the pistons 36 will be on their inward or suction strokes in all of the cylinders 21 whose corresponding hollow arms 32 have their ports 33 in communication with the port I I6. Fluid will, therefore, be sucked up through the port I I6, through the ports 33, the ports 28 and into the cylinders 21. At the same time the other pistons 36 will be on their outward or exhaust stroke in all cylinders whose corresponding ports 33 are in communication with the port I I1, so that fluid under pressure will be forced out of the cylinders 21, through the ports 28, the arms 32 and the ports 33 into the port I I 1 from whence it will travel to the motor B through the passages I22. Such pressure fluid will pass through the member I6, the member I0 and the member I8 into the port I20.

The operation of the motor B may be broadly described as similar but opposite to that of the pump A. Pressure fluid entering the port I 20- will enter all the ports I04 that are then in communication with it and will travel through the corresponding arms I03 and the ports I92 into the outerends of the cylinders 98. Pressure will thusbe exerted upon the pistons I01, the con necting rods I08, the ring IIO, the bearings H3 and will react against the spindle 9I. As this spindle is positioned eccentrically to the axis of the rotor 82, the rotor will be caused to turn in a clockwise direction and the driven shaft 88 will thus be operated. As the stroke of the motor pistons I01 is fixed, the speed of the rotor 82 will depend upon the quantity of oil supplied by the pump A and as this may be varied from zero to maximum, the speed of the rotor 82 may similarly these cylinders will be expelled, passing throughv be varied. At the same time, the pistons Ill 1 will be on their outward or exhaust stroke in all the cylinders 98 whose corresponding ports I88 are in communication with the port II9, so that fluid in The entire operation of the pump A will thenbe-reversed, pressure fluid being forced into'the port II6, through the passages I2I, into the port II9, where it will enter the ports I04 in communication with it and will cause the rotor 82 to rotate in a counter clockwise direction. The direction of rotation and the speed of the rotor 82, therefore, depend entirely upon the position of the crank pin 56. I

Any suitable means may be employed for shifting the slide 55 and hence of moving the above described crank pin mechanism, as for example, a screw and nut device of well known design.

As illustrated herein I have shown hydraulic power means for accomplishing this result, and have provided at each side of the machine and suitably secured to the end plate I2 cylinders 16 closed at their outer ends and containing pistons 11- connected to plates 18 secured at 19 to the slide 55. Fluid pressure conducting pipes 88 enter the outer ends of these cylinders. Fluid under pressure for operating these cylinders 16 may be secured from any preferred source, as

froma separate pump, and controlled by any suitable valve control device. I prefer, however, to obtain pressure fluid from the main or working circuit of the transmission device and this is accomplished through and controlled by the valve mechanism located in the valve block I42. This valve block is the same as that shown in Figs. 8 to 12 of Letters Patent of the United States granted to Charles M. Manly on November 28,1916, No. 1,206,453, and need not be described here in detail, but'contains, among others, valves for continuously furnishing pressurefluid to an adjusting valve bywhich the admission of pressure fluid to either of the cylinders 16 may be controlled. For controlling the adjusting valve I have shown a floating lever device comprising a link I5I (see Fig. 1) attached on one end to the stem of the adjusting valve and on its other end movably-attached to the lever I52. The other end of lever I52 is movably'connected to the rod 8| which in turn is rigidly fastened to the slide 55, projecting through a passage in the casing 13.. Means for operatingfthe floating lever device is indicated at. I53 in Fig. 1.- In operation-of thist control; an impulse applied to the lever I52 by means of the element I53 will cause the rod I5I to be pushed in or'pulled out as the case may be. In one instance the adjusting valve will be so moved as to permit pressure fluid to pass through one of the pipes 88 into one of the cylinders16 where it will react against the piston 11 and shift the slide 55 and the crank pin 56 in one "direction. When the rod I53 is moved in the opposite direction, pressure fluid will be permitted to 'pass throughthe pipe 88 into the other cylinder 18.

and the slide 55 'andcrank pin 56 will conse-- quently be moved in the opposite direction. In

either direction, the floating lever device acts as a follow-up to shut off the pressure fluid when' the slide 55 has been moved the amount-corresponding to the distance the element I53 has been moved.

In devices of this class, leakage is bound to occur as it is a physical impossibility to have the working parts fit so snugly as to entirely prevent it. Consequently, I have provided for collecting and returning such leakage, and, for convenience, I shall use the term leakage circuit to broadly designate the mechanism through which this is accomplished.

One embodiment of such a leakage circuit is" shown in Figs. 1, 2, 4, and 5. I provide cooling tanks I29 and I3I which are connected for free interconnnunication by the pipe I32 and which are-secured to the stationary parts of the machine in any suitable manner. These tanks are preferably located at a point relatively low with respect to the pump A and the motor B so as to facilitate the collection of leakage as will be later described. They are also preferably placed near the outer ends of the rotating pump cylinders 21. They may be of any desired and practical size and shape, but I prefer to make them large enough to contain substantially more fluid than the leakage fluid collected therein, so that there will be a reserve supply at all times for replenishing the main fluid system and also so that fluid may be temporarily halted therein, thus allowing it to be cooled by the air currents stirred up by the rotating cylinders 21. As shown these tanks are of somewhat curved cross section, enabling a greater area to be positioned close to the path of the rotating cylinders. They may be made of any suitable material,'butare preferably made of aluminum or thin copper, because of the heat conducting properties of these metals and to reduce weight. Radiating fins may be added if de between webs I18 and I19 is free to pass into the intercommunicating chambers I15 in the member- I0. When fluid accumulating in the cham-' bers I15 reaches the level of the overflow duct I21 it will pass through this duct into the pipe I28 and then into the pipe I32 which is connected with tanks I29 and I3I. The overflow duct I21 may be located at any desired point below the passage I25, but I prefer to place it at about-the level of the upper surface of web I19.

so that considerable fluid may accumulate in the chambers I15, absorbing and'carryingaway heat from the member III. The level of the fluid in the rotor casing 82 is determined by the position of the passage I23. I

Fluid leaking from around the members I6 and I8 on their ends nearest the member III will'pass through the aligned passages I33 in the whence it is free to flow into either of the tanks I 29 and I3 I.

Fluid leaking from around the valve member I6 at its end nearest the pump cylinders 21 will leak through passages (not shown) in the plate 41 and into the rotor casing I9. Fluid leaking from the inner ends of the pump cylinders 21 will find its way around the crank pin mechanism and into the rotor casing I9. Fluid thus accumulated in the rotor casing I9 will overflow through the open spider 5| into the space I4 at the bottom of the casing I3 from which it passes through a passage I30 into the tank I29. v

,.It will be observed that all of the fluid leaking from the various parts of the main or working circulatory system is eventually accumulated in the cooling tanks I29 and I3I. Positive means for returning this leakage is provided and comprises a pump I31 driven from the drive shaft 43 by some suitable means such as a chain I38 trained about a'sprocket I39 on the shaft of the pump I31 and about asprocket I49 mounted on the drive shaft 43. This pump may be of any-preferred type and is hereillustrated as a gear pump of a well known type and is made of a capacity large enough to supply at all times an excess of fluid over and above the amount needed to replenish the leakage in the main or working circulatory system. The suction side of the pump I31 is connected through a pipe I36 with the tank I3I. The pressure or discharge side of the pump I31 is connected to a pipe I4I through which fluid under pressure is conveyed to the valve block I42. As hereinbefore noted, this valve block may be the same as that shown in the patent to Manly, No. 1,206,453. It contains valve mechanism through which fluid delivered to it by the pumpv I 31 is admitted to the main circulatory system to make up for the fluid which has leaked out and maintain the volume of fluid therein substantially constant. Pipes I43 and I44 connect the valve distributing mechanism in the valve block with the passages I45 and I46 respectively in the member I9, the latter passages passing through the webs I19 and I18 and communicating with the passages I22 and I2I respectively of the main circulatory system. The replenishing fluid will be fed alternatively into passages I2I or passages I22, that is into whichever pair of these passages is at the time serving as the low pressure or return passages of the main circulatory system. The setting of the spring on the blow off or'exhaust valve I16 in the valve block determines the pressure built up by the pump I31 and hence the maximum pressure maintained in the low pressure passages of the main circulatory system; in practice it has been found that the best results are obtained when this pressure is kept at higher than atmospheric pressure, the exact amount varying with, individual installations and conditions.

The excess fluid delivered to the-valve block I42 by the pump I31 and not required for replenishing the main circuit or other purposes will be discharged through the blow off valve I16 through the passage I11 in the member I9 and will enter one of the intercommunicating chambers I15 whence it will return to the tanks I29 and I3! in the manner hereinbefore described.

Another and improved embodiment of my leakage circuit is shown in Figs. 9, 10 and 11. It embodies in novel manner the preferred features of a positive pressure replenishing system, broadly similar to that previously described, and of a gravity replenishing system whereby replenishment is accomplished through inwardly opening check valves acting under suction from within the main circulatory system and from the weight of the column of fluid in an elevated reserve tank.

The pump I31 and the method of driving it are the same as hereinbefore described. The pressure or delivery side of this pump is connected to the pipe 24I. Located on the top face of and suitably secured to a modified form of the member I0 is a member 242 in which are formed a pressure chamber 243 and a reservoir 244, closed at their tops by the cover 245 in such a manner as to form fluid tight joints with the walls of the pressure chamber and of the reservoir. Fluid under pressure delivered by the pump I31 passes through the pipe 24I and enters the pressure chamber 243 through the port 246 which is preferably placed near the top of one of the walls of thepressure chamber so as to prevent fluid draining out of the chamber when the pump I31 is stopped. Located in the bottom of the chamber 243 are two check valves 246 and 241. Valve 246 is connected with the passage 248 in the modified form of the member I0, this passage intersecting and connecting the pair of passages I22 of the main circulatory system. Similarly valve 241 is connected with a pair of passages I2I through the passage 249. The check valve 246 is designed to open and admit fluid from the pressure chamber whenever the pressure in the chamber 243 exceeds that in the passage 248 and hence in the passages I22, but when thepressure in the passage 248 exceeds that in the chamber 243 the valve 246 will close and prevent any fluid passing into the chamber 243. Valve 241 operates in the same manner.

Controlling the pressure in the chamber 243 is an exhaust or blow-01f" valve 259 located in the wall of the chamber adjacent the reservoir 244. This valve is preferably placed near the top of the chamber 243 so that any air that enters may rise and be quickly expelled. As shown, the valve 250 is of the piston type and is held on its seat by a spring 25I mounted on a suitable support as 252. The spring 25I may be made adjustable or may be set for any desired pressure. When the pump I 31 is in operation the force placed on the valve 250 by the spring 25I determines the pressure maintained in the pipe 24I and the chamber 243 and hence the minimum pressure in passages 248 and 249 and the passages I2I and I22 of the main circulatory system. Pressure fluid will, therefore, replace leakage in the main circulatory system and maintain in it a. predetermined pressure. When the pump A is at its no stroke position, replenishing fluid may be supplied simultaneously to both of the pairs of passages I2I and I22 and any deficiency of fluid in the main circulatory system will be quickly made up. When the pump A is given stroke the pressure generated by it will exceed that in the chamber 243, under ordinary conditions, and the check valve 246 or 241 will out 01f communication between the chamber 243 and whichever of passages I2I or I22 is then constituting the path of. travel of the high pressure fluid from the pump A to the motor B; but leakage will be replenished through whichever of these passages I2I or I22 is then constituting the low pressure or return side of the main circulatory system. When the pumps A and I31 are stopped, the chamber 248 will be completely filled with fluid. If leakage occurs in the main circulatory system as the machine stands idle, one or, both of the valves 246 and 241' will open under the weight of the fluid in the pressure ervoir 2. Located near the opposite end of .the reservoir is an overflow wall 253 which may be of any desired height but should below enough to permit the easy flow of fluid between its top and the cover 245. Located between the walls.

253 and 255 is a compartment 254-which is connected with a passage 256 in the modified form of the member It. This passage 256 leads into a cooling tank 251, here shown as secured to the lower face of the member I8. This tankis preferably placed low enough to facilitate the collection of leakage and adjacent the rotating pump cylinders 21 so that it may be cooled by the air currents generated by them. Positioned below the passage 256 inthe tank 251 is a curved baflle plate 258 which retards the speed of fluid entering the tank through the passage 256 and thus prevents turbulence. An air vent 259 is located near the top of one wall of the-tank 251. A strainer 26! is placed in the tank at an angular position, one of its endsbeing supported by the bailie plate 258 and the other end resting in the opposite bottom comer of the tank 251. The angularposition of the strainer makes it possible to have all incoming fluid enter the tank above the strainer while maintaining a good head of fluid above the port 262, and also allows the fluid to pass through the strainer slowly and gradually, thus eliminating both dirt and air from, the fluid. Connected to the port 2162 is the-pipe 268 which leads to the suction or intake 7 side of thepump I81.

shown, connected in turn described, such leakage being conducted into the tank 251 through suitable connections, one or which is indicated at 268 which is a port in the wall of the tank 251 connected to. a pipe, not with the space" in casing l3. I

The circulation of the fluid will be clear from the foregoing description. The speed of the fluid discharged through the valve 250 will be checked by'the valve support 252 and by the fluid already in the reservoir. If any air has become mixed with the fluid, de-aeration will begin to take place in the reservoir and will continue as the film of fluid flows down the wall 253 and the passage 256.

In some instances it is desirable to maintain one or both rotor casings completely filled with fluid as this retards/leakage, particularly when the-machine stands idle, and assures proper lu-,

brication of allparts at starting. A serious objection to this in other devices of this class has been that the rotating parts churned the fluid and generated considerable heat. Astherotor casings in my devicerevolv with the other roonly churning effect, therefore, is the small.

formed in the modified form of the member In.

Another yertical passage 261 leads from the bottom of the chamber 266 and is connected with the longitudinal passage I26, Figs. 2 and 9, which passes through the member 18 and the member l8 and connects with the passage I23, one end or which is open to the interior of the rotor casing 82. Fluid in the reservoir 2 will flow through the passage 265, into the chamber 266, the passage 261, the passages I26 and I23 and into the rotor casing 82, completely filling all of them. Leakage occurring from the inner ends of the cylinders 98 and from the end of the valve member l8 nearest them will cause a slight pressure in the rotor casing, causing the excess fluid to rise through the various communicating passages into the reservoir 2 and from there it will return to the tank 251 in the manner already described.

Either or both of the pump and motor units disclosed herein will function as either a pump or motor, with a variable or fixed stroke as desired, and either unit may be used in connection with two or more of the other units, suitable changes-for this purpose being made in the intercommunicating means.

Having thus described my invention, I claim: 1. In a hydraulic power transmission apparatus, the combination of relatively and independently'rotatable pump and motor units, a station ary valve device supporting and establishing communicationtherebetween, said units and said said liquid circulation system, and means 'ior cooling the collected liquid by utilizing the-curi rents of air produced by said rotating mem- Leakage will be collected in the manner already bers.

2. In a hydraulic power transmission apparams, the combination of pump and motor units at least one of which comprises a plurality of rotating cylinders exposed to free air and independently rotatable with respect to said other unit, a main fluid circuit for connecting said pump and motor, an auxiliary fluid circuit comprising means for collecting fluid leaking'from said main circuit, means for supplying make-up fluid to said main circuit from said fluid-collecting means, and means for cooling the fluid in said auxiliary circuit by utilizing air currents set in motion by said rotating cylinders.

3. In a hydraulic power transmission device, the combination of a main fluid circulatory system, comprising pump and motor units'at least 6 one of said units having a number. of radially arranged rotary cylinders freely exposed to the atmosphere and independently rotatable with respect to said other unit, a secondary fluid circuit including means for collecting leakage fluid and returning it to said main circuit, and a storage tank in said secondary circuit located in a position to be fanned byfthe air currents setup by said rotary cylinders. v 4. In a hydraulic power transmission device,

"a liquid circulation system comprising rotary:

' unit and having pistons operating within the inner, ends thereof and having their outer ends closed, each of said trunnion-like valve members having a plurality of ports, and each of said cyl- 'comprising a main circulatory system including pump and motor units and inter-communicating valve, a liquid storage chamber, means for re-- turning liquid leaking from said main circula- I tory system to said storage chamber, a pressure chamber communicating with said storage cham ber, means for forcing liquid from saidstorage chamber to said pressure chamber,- a plurality, of passages communicating between said pressure chamber and said valve and an overflow tank communicating with said pressure chamber, said overflow tank having a lateral partition extending part way to the top of said chamber, a pas-. sage communicating from one side of said partltion with the crank case for said motor, and a second passage communicating from the other side of said partition with said storage tank.v

- 6. In a hydraulic transmission having a fluid circuit and comprising a. pump unit and a motor unit, one of said units having a rotary cylinder element providediwith a rotary valve chamber in axial alignment therewith, reciprocating pistons in the cylinders of said cylinder element, a stationary member positioned adjacent said one of the units, a cylindrical valve element extendin from said stationary member and entering said valve chamber, a crank pin to which said pistons are operatively connected, and means-for supporting said crank pin entirely upon said cylindrical valve element.

7. A hydraulic power transmission apparatus comprising a central stationary member provided with a pair of opposed trunnion-like valve members, and independently rotatable pump and motor units mounted for" rotationabout said trunnion-likevalve members, each of said units comprising a rotor provided with a plurality of radial tons of said motor unit also'supportedon said trunnion-like valve member, means connecting said' valve members to join said pump and motor units in a closed fluid circuit, and means Ior varying the stroke of the pistons in said pump unit in order to control the speed oi the motor unit.

8. In a hydraulic transmission having a fluid circuit and comprising a pump 'unit and a motor unit, one or said units comprising a plurality of cylinders radiating from an interior space, pistons reciprocable in said cylinders, and a rotary element provided with an axial 'chamber to which said cylinders are connected, a cylindrical valve element entering said axial chamber and conveying fluid to and from said unit, and an auxiliary fluid circuit for collecting and returning leakage fluid. said auxiliary circuit comprising means embodied in said valve element for conveying outwardly from the interior space fluid that has leaked past the pistons into said space.

9. In a hydraulic transmission having a main fluid circuit and comprising a pump unit and a motor unit, one of said units having a cylinder element independently rotatable with respect to the, other of said units, said cylinder element being provided with a valve chamber in axial alignment therewith and having cylinders exposed to free air, a cylindrical valve element entering said valve chamber and conveying fluid from said main circuit to and" from said unit, and an auxi1- iary' fluid circuit comprising fluid connection with the interior of said rotary cylinder element for conveying fluid inwardly and outwardly therefrom, said fluid connection being embodied insaid valve element.

10. In a hydraulic transmission havinga fluid circuit and comprising a pump unit and a motor unit, one of said units having a rotary element including cylinders exposed to free air, a stationary member positioned adjacent said unit, a valve element carried by said stationary member and establishing fluid connection with said rotary element, a fluid-leaking running joint between said valve element and said rotary element, unitary means for enclosing said running joint and for collecting fluid leaking through said joint, and means for returning fluid so collected to the fluid circuit.

11. In a hydraulic transmission having a fluid circuit and comprising a pump unit and a motor unit, one of said-units having a rotary cylinder element provided with a rotary valve member in axial alignment therewith, reciprocating pistons inthe cylinders of said cylinder element, a stationary member positioned adjacentsaid one of the units, a valve element supported on said stationary member and coacting with said valve member to-control the flow oi fluid for said cylinders, a crank pin to which said pistons are operatively connected, and means for supporting said crank pin entirely upon said valve element.

Hp'oo A. CEN'I'ERVALLZ 

